Differential stage lift flow device



June 8, 1943.

A. BOYNTON DIFFERENTIAL STAGE LIFT FLOW DEVICE Filed Dc. 8, 1939 3 Sheets-Sheet l ATTORNEYS.

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A. BoYNToN DIFFERENTIAL ASTAGE. LIFT .ILow DEVICE Eiled'neo. e, 1939' 3. Sheets-Sheet 2 ALEXANDER Boy/v 70N, /A/V N70/2,

ATTORNEYS,

mg. 11. Fig. 10.

.um s, 1943. A. BOYNTQN 21,321,003

DIFFERENTIAL STAGE LIFT FLOW DEVICE A rr'o/M/E rs.

Patented June 8, 1943 UNITED -sTATEs PATENT OFFICE DIFFERENTIAL STAGE LIFT FLOW DEVICE Alexander Boynton, San Antonio. Tex.

Application December 8, 1939, Serial No. 308,318

Claims. (Cl. 137-7111) means embodying a time element and a force element and a combination of such elements.

Another object is to provide a, pressure fluid valve that will close quickly and open quickly, if and when such action is necessary.

For such purposes, I employ a differentially operated valve actuated by a piston contacting the pressure fluid and having another piston mounted on the same shaft with the rst piston and the pressure fiuid valve. A spring normalllr urging the pressure fluid valve away from its seat is employed in conjunction with a stationary latch and a check valve mounted between the movable pistons which confine a lubricant between them. A balile is also provided to prevent abrasive substances in the pressure fluid from cutting the valve member.

The foregoing objects are attained by mechanism herein described and illustrated by the accompanying drawings, in which,

Fig. 1 is mainly a longitudinal section through the preferred embodiment with the pressure uid valve open. part of the tubing nipple being shown in outside view.

Fig. 2 is a cross section on the line 2 2, Fig. 1. Fig. 3 is a longitudinal section through a part of the mechanism shown in Fig. l with the pressure fluid valve closed and a latch employed.

Fig. 4 is a cross section on the line 4 4, Fig. 3. Fig. 5 is a cross section on the line 5 5, Fig. 1. Fig. 6 is a cross section on the line 6 6, Fig. 1. Fig. 7 is a cross section on the line 1 1, Fig. 1. Fig. 8 is a cross section on the line 8 8, Fig. 1. Pig. 9 is a partial longitudinal section and outside view illustrating a modified form of pressure fluid valve and seat.

Fig 10 is mainly a longitudinal section through -a modification of the invention.

Fig. 14 is a cross section on the line Id-M, Fig. 11.

Fig. 15 is a cross section onthe line |5 |5, Fig. 10.

Fig. 16 is a installation plan of a surface intermitter partly in longitudinal section and partly in outside view.

Fig. 17 is a cross section on the line H-Il, Fig. 16.

Fig. 18 is an installation plan of the flow devices y in a well.

Each of the prime sections will be understood as identical with the unprimed section bearing the same reference numerals, except that some of the parts cut are different in other respects from the place shown in the sections.

Similar reference characters are employed to refer to similar parts throughout the several views of each embodiment.

The differentials will be understood to be the diierence in pressures obtaining in the well within and without the well tubing.

The column of well liquid caused to stand up in the tubing above the depressed liquid level between the tubing and the casing will be referred to as the upstanding column.

Expulsion of liquid from the well will be understood as caused by expansion of pressure fiuid admitted into the upstanding column by the flow devices.

The pressure fluid valve, the metering sleeve.

the two pistons, the spring between them and the f.

The flow devices will be understood as spaced approximately 200 to 300 feet apart in the flow tubing.

The differential force per square inch required to seat the pressure fluid valves ordinarily will be somewhat greater than the force ,per square inch exerted by a column of the unaerated well liquid twice as high as the distance between adjacent devices.

In Fig. 1, illustrating the preferred embodiment, the tubing nipple I is adapted to be threadably joined into the tubing string, as appears in Fig. 18. The upper sleeve 2, having the projection 2a., is pressed over and secured upon the nipple l by means of the welds 2b. The sleeve 3, having the projection 3a, likewise, is pressed over the nipple I and secured upon it by the peripheral welds 3b and 3b'.

The bushing 5, having threaded connection Within the upper portion of the projection 3a, has

its lower end firmly engaged upon the upper endl of the valve seat member I which is thereby hermetically engaged upon an annular shoulder surrounding the upper extremity of the chamber 8c within the projection la. The shell 8 is threadedly joined over the upper portion of the bushing 5 and has its upper end threadedlyjoined over the cap I9. The stud 2|, having threaded engagement within the extension 2a, has its lower conically tapered end engaged centrally within the cap I9 for the purpose of securing the shell 6 aligned with the nipple I.

The lower piston 8 has a depending extension 8a upon the lower end of which the valve 8b is formed and adapted to engage the seat la to close the central opening 8b ot the member 4 when the device is not intaking pressure uid. The rod I6, slidable through the check valve member I4 and within the central opening through the upper end of the member I8, has threaded connection with the pistons 8 and I1, both pistons being closely slidable within the shell 6. The lock nut 29 may be employed to secure together the rod I6 and the piston I1.

The packing rings 9 and I8, which may be of leather or metal, may be employed to cause the slidable pistons 8 and I1 to have hermetic engagement within the-she1l 6. The recess I1a and the openings I1b provide that pressure fluid will force the ring I8 outward in contact with the shell 6. The recess 8c and the openings 8d, likewise, provide that a lubricant within the chamber 6e will force outward the packing ring 9 and also make hermetic the sliding engagement of the piston 8 within the shell 6.

The support nipple I0 may be Dressed into the shell 8 and secured thereby the set screws II engaged within the triangular recess I0c (see Fig. 3). The slight coiled spring I3 supports the check valve I4 yieldably engaged against the nether side of the plate-like top of the member I0, having the openings I0a normally closed by this valve, except for the slight clearance llb- The bushing I2, having the openings I2a, is threadedly engaged within the lower end of the nipple I0 to provide a support for the spring I3. The check valve I l has a thin walled depending tubular extension Ila closely slidable over the rod I8 and within the bushing I2. This exten-- sion passes through the bushing I2 in order to provide a smooth surface confronting the spring I3 which surface will not become impinged upon the coils of this spring, as might happen if the extension Ida had its lower end above the bushing I2.

The metering sleeve 1, having its upper end threadedly engaged over a depending portion of the piston 8, is closely slidable within the restricted bore of the shell 6 immediately below the annular shoulder Bb. The coiled spring I5. havirg slight clearance within the shell 6 and having its lower end engaged upon the nipple IIJ, resiliently urges the piston I1 against the cap I9 and positions the metering sleeve 1 and the valve 8b as shown in Fig. l.

The lower end of the metering recess 7a normally is positioned slightly above the horizontal opening of the chamber 6c when the piston I1 ls engaged with the cap I9. When the valve 8b is closed upon its seat la, the upper end of the recess 1a is somewhat below the horizontal opening of the chamber 6c. In this manner, communication is c ut off between` the openings Ba and 1b when the movable assembly is in the upper position as in Fig. 1. and is .also cui 911? `which produces the dilerential.

when the movable assembly is in the lower position as in Fig. 3.

The annular metering recess 1a, being tapered to a feather edge at its upper and lower extremities. it is apparent that the greatest volume of pressure fluid will pass from the openings ia into the openings 1b when the valve 8b is approximately half way of its travel, i. e.. during one-halt of the differential required to seat the valve 8b.

It will be observed that the upper and lower tapers upon the member 1 which form the recess 1a are convex in order that this recess will meter the flow of pressure fluid in proportion to the load to`be lifted by it.

The baille 5a deects the flow of pressure iluid entering through the openings 8a and directs it through the annular chamber 6c in order to prevent the metering sleeve 1 from being abraded by foreign substances often present in the pressure iluid. y

The chamber 6e between the pistons 8 and I1 may be filled with a lubricant which will ride between the pistons during the movements of the movable assembly. In this manner, lubrication is provided for the pistons and all moving parts between them. This lubricant also lubricates the check valve I4.

The pressure fluid force entering the chamber 6d through the openis I9a actuates the piston I1 and compresses the spring I5 whenever the upstanding column of well liquid within the tubing exerts a pre-determined less force than that oi the pressure fluid exterior of the tubing. 'Ihe compression force under which the spring I5 is installed determines the differential at which the piston I1 will begin moving downward and the total force required to compress this spring far enough to seat the valve 8b determines the operating differential of the ow devices.

It will be observed that each of the discharge openings below the valve seat 4a is many times larger than the intake openings 6a and 1b. This relation is necessary in order to maintain less pressure than that of the pressure fluid within the chamber 5b until the valve 8b is seated.'

The openings 'Ic serve no other purpose than to alford circulation into and out of the annular space 1e between the annular shoulder 6b and the piston 8 as this piston moves.

The spring I5 and the pressure iiuid within the annular space between the well casing and the ilow tubing exert constant forces, while the upstanding column exerts the variable force The spring I5 and the upstanding liquid column exert the valve unseating forces, while the pressure iluid exerts the valve seating force. l

The path ofthe pressure fluid out of the annular space between the casing and the tubing and into the upstanding liquid column in the tubing is via the lateral openings 6a, the annular chamber 6c, the metering recess 1a, the openings 1b, the annular space 1d, the chamber 5b, the central opening 4b, the chamber 3c, and the opening 3d. This path, preferably, is closed, as before stated, when the movable assembly is in its extreme upper position, as in Fig. 1, and also in its extreme lower position, as in Fig. 3. The metering recess 1a, however, may be lengthened at either or both ends to vary the metered flow of pressure tluid as may be desired.

All diil'erentially operated ilow devices will have their valve action disturbed by momentary .false differentials resulting from slippage within the tubing. The impact of heavy falling slugs of well liquid will often force open all valves in the devices below the places of such impacts; The inrush of pressure uid then will frequently expel the well liquid from the tubing as a slug. The resistance of such slugs impelled by excessive quantities of pressure fluid will kick open all higher valves as they pass them. This results in a waste of -energy and greatly impairs the usefulness of differential iiow devices, particularly so in deep wells.

The check valve I4 prevents the valve 8b from being suddenly forced open by false differentials.

This check valve, however, does not retard the seating action of the valve 8b'. During the downward movement of the movable assembly, the piston I1 forces some of the lubricant within the chamber 6e through the openings Illa, unseating the check valve I4. This displaced lubricant continues downward through the annular chamber Illb and passes through the openings I2a into the chamber above the piston 8. But after the valve 8b seats, the lubricant entrapped under the nipple I and the bushing|2 -an'd above 'the piston 8 cannot escape back into the chamber 6e, except through the slight clearance I4b which prevents the check valve I4 from completely closing the openings Illa. This clearance should be slight enough to so impede the passage of the entrapped lubricant that the valve 8b will not recede Vfar enough from its seat 4a to move the metering recess 1a upward so far that it will intake pressure fluid before the false differentials, tending to unseat -the valve 8b, have subsided. In this manner, an even flow of pressure fluid is provided during the prevalence of true differentials and the devices are prevented from intaking pressure fluid at all other times.

In Fig. 3, which illustrates the closed position of the valve 8b, the check valve I4 is shown still open, due to the fact that the valve Sib-has just closedvandathe check valve h-as not had the instanti'of time necessary to assume its normal closed position as in Fig. 1. A latch, however, has been added, consisting of the latch balls 22, the ball roof 23, and :the ball oor 24. The latter member m-ay be free within the shell 6 or it may be pressed in upon the member .IIL The peripheral slots 23a of the ball roof 23, and 24a of the ball floor 24, provide for free circulation of the lubricant within the chamber 6e between the pistons. The ball roof 23 must have some clearance within :the shell 6 in order that the latch will be free.

The latch shaft 25, slidable through .the members I0, 23, I4 and 24, has a portion of restricted diameter 25a Within which the latch balls 22 are adapted to engage when the valve 8b is seated,

l as appears in Fig. 3. The latch balls are urged inwardly by the confronting inclined surfaces of the ball `roof 23 and .the ball floor 24, which surfaces engage the balls in both the engaged and the disengaged positions of the latch.

The shaft 25 has its upper extremity threadedly engaged within the.piston 21, corresponding to the piston I1 in Fig. 1, where it may be locked by the set plug 26 in proper position to cause the latch to be properly engaged when the valve 8b is seated.

In Fig. 9, illustrating a modified form of pressure uid valve and seat, the piston and valve member 28 has its lower end formed into the valve 28a adapted :to engage upon the valve seat 29a of the valve seat member 29. The openings 23h serve thc same purpose as the openings 4b in Fig. 1.

In Fig. 10, illustrating another modified form of the invention, the tubing nipple I has the upper sleeve 2 pressed over it and secured upon it by the welds 2b. 'I'he lower sleeve 30 is also pressed over the nipple I and secured toit by the welds 30D. Likewise, the intermediate sleeve 3| may be pressed over the nipple I and secured to it by the peripheral welds 3Ic and 3 Ic.

The nipple 34 isthreadedly joined into the upper end of the projection 3Id of the sleeve 3|. The internal annular shoulder 34c engages upon the upper end of the valve seat bushing 35 holding it rmly and hermetically engaged upon the annular shoulder 3 le of the member 3|.

The upper shell 33, having threaded connection with the nipple 34, has i-ts upper end engaged with the support cap 39, having the tubular extension 39a threadedly engaged Within the projection 2a of the sleeve 2 for the purpose of securelly aligning the shell 33 with the tubing nipple The nipple 40 has threaded engagement within the lower end of the projection 3Id of the member 3l and with the lower shell 32 having its lower end hermetically closed by the cap 48. This cap has a coun-tersink in its lower end within which .the tapered upper end of the securing stud 49 is engaged by means of its threaded connection through the projection 30a of the member 30. This stud serves to secure the alignment of the shell 32 and cap 48 with the tubing nipple I.

The valve rod 36 threadedly engages centrally through the piston I1 to which it m'ay be further secured by the lock nut 38. The valve 31 may be pressed over the rod 36, landed upon the enlargement 36a, and secured there by the weld 31a. The un-tapered portion of the valve 31 may be of the same length as the untapered openings 34d and 35d. Within the latter opening, this valve has a closely slidable valve fit. The upper end of the metering chamber 34h is also untapered, like the straight portion 35d of the chamber 35, and also closely receives the valve 31 with I a slide valve t.

The valve rod 36 has a lower enlargement 36h formed into a valve which seats upon .the upper surf-ace of the valve ring 4I which ring has its outer surface formed into a valve engageable with the valve seat vformed upon the lower end of the nipple 40. I

The ball floor 44 has threaded engagement within the shell 32 and may be locked in proper posi-tion by the lock ring 46. The latch balls 45 are adapted to be urged inwardly by the confronting inclined surfaces of the members 43 and 44 engaging the balls. The coiled spring 42, having slight clearance -Within the chamber 32a, has its upper end engaged under the valve ring 4I and its lower end engaged upon the ball roof 43 having some clearance within the shell 32. This spring, preferably installed under some compression, is further compressed when the valve 31 engages its seat 35a and provides the latching force when the balls 45 engage within the latching recess 36e.

The check valve 41 has a central opening through which-the lower portion of the rod 36 is received with the slight clearance 41a. The upper inner surface of the cap 48 is formed into a seat for the valve 41.

The valve rod 36 is normally positioned by the engagement of the enlargement 36h upon the valve ring 4I, there being then some slight clearance between the lower' end oi the cap 39 and the piston I1.

Pressure fluid force entering through the opening 39D contacts the piston I1 closely slidable within the chamber 33a and forces it downwardly with the valves 31 and 4I, thereby compressing the spring 42 and engaging the latch balls within the recess 36o when the valve 31 closes upon its seat 35a. The piston I1 has clearance with the tubular baille 34a when the valve 31 is seated at 35a.

The path of the pressure fluid entering the tubing is via the openings 33h, the annular barile chamber 33e, the metering chambers 34h and 35b, and the openings 35e, 3Ia, and 3Ib. In this connection, it will be observed that there will be no flow of pressure fluid through the device at the beginning of the valve travel and no flow at the end of the valve travel, because, as previously stated. the valve 31 is closely received within the upper end of the metering chamber 34h and within the lower portion 35d of the metering chamber 35h.

The tubular baiile 34a is designed to withstand the abrasive action of the pressure fluid entering the device, and thereby protect from abrasion the rod 36 and the valve 31.

It is apparent that the openings 33h should be much smaller than the valve 31 in order that proper differences in pressures will obtain above and below the piston I1 when the device is in operation.

The chamber 32a may be filled with a lubricant which cannot escape, due to the normally seated ring valve 4I and the closely slidable t between the ring valve 4I and the rod 36 which will retain the lubricant in all positions of the device before it is placed in service.

The valve 31 may seat freely in response to the greater pressure above the piston I1 than that below it and in further response to the greater pressure above that valve than that below it, because the valve ring 4I has large clearance with the shell 32. While the valve 31 is moving toward its seat 35a, the lower end of the rod 36 is entering and displacing part of the lubricant within the chamber 48a. During this displacement, the check valve 41 will be raised by the lubricant under it and this displaced lubricant will pass upwardly through the large clearance around the member 41 in its raised position and through the small clearance 41a, continuing upward through the large clearance which the rod 36 has with the lock ring 46, the ball floor 44 and the ball roof 43.

The upward receding movement of the valve 31 from its seat 35a is impeded by the latch and by the check valve 41.l This valvel which rises while the upper valve 31 is seating, then closes immediately by gravity and resists the upward movement of the rod 36, because the lubricant seeking to compensate for the withdrawal of the rod out of the chamber 48a must move into this chamber through the small clearance 41a.

In summarizing the unseating action of the pressure fluid valve, it will be noted that the latch, in exerting' a pre-determined force in holding the valve 31 seated, supplements the differential in causing a leakproof engagement of that valve upon its seat. The check valve 41 exerts no seating force upon the valve 31 but supplements the force of the latch with the time element developed by resisted migration of the lubricant. The straight portion 35d of the metering chamber 35h brings in another time elementin opening the valve 31, because that valve cannot admit pressure fluid through the device until the latch springs and enough lubricant passes downward through the slight clearance 41a to allow the valve 31 to pass out of the straight portion 35d of the chamber 35h.

Part of the lubricant within the chamber 32a must pass around the ring valve 4I and into the chamber 40a during the downward movement of the rod 36. The restriction 40h, through which the enlargement 36h of the rod 36 has slight clearance, and the chamber 40a are interposed between the displaced lubricant and the path of the pressure fluid through the openings 3I a and 3Ib in order to prevent the displaced lubricant from being blown out into the tubing.

For convenience in adjusting the device, it will be observed that after rst removing the piston I1, the rod 36 may be withdrawn through the opening 39h. The piston may be made accessible for removal by screwing the tubular extension 39a upward in the projection 2a. The latch may be also adjusted by screwing the ball floor upward or downward, as is apparent.

In Fig. 11, illustrating another modified form of the invention, many parts are the same in form` and purpose as in preceding embodiments, and for that reason some such parts will not be discussed further.

The sleeve 6I may be pressed over the tubing nipple I and secured upon it by the peripheral welds 6Ib and 6Ib'. The nipple 52, having threaded engagement within the projection 6Ia of the member 6I, has its internal annular shoulder 52e` rmly engaged upon the valve seat member 53, which is thereby forced into hermetic engagement upon the internal annular shoulder 6Ic. The upper shell 33, having threaded engagement with the nipple 52, has its upper end engaged by the support cap 39.

The lower shell 62, having threaded engagement within the projection 6 I a, is closely slidable through the tubular projection 60a of the lower sleeve 60 secured upon the nipple I by the welds 60h. The lower end of the shell 62 is closed hermeticaily by the plug 59.

The piston I1, threadedly connected to the rod 50 and further secured upon it by the lock nut 20, is closely slidable within the chamber 33a of the shell 33, the packing I8, expanded by the pressure fluid entering through the openings IIa and I1b serving to prevent leakage past this piston.'

The plunger 5I, having its upper metering pin 5Ia threadedly engaged with the rod 50 and having its lower metering pin 5Ib threadedly engaged with the rod 54, preferably is positioned within the chamber 52h so that there is approximately the same clearance space between the pin 5Ia and the portion of reduced internal diameter 52a as the pin 5Ib has within the opening 53h when the valve 5Ic is halfway of its travel toward the seat 53a. The greatest diameter of the pin 5Ib is slightly less than the diameter of the opening 53h. The plunger 5I has the valve 5Ic formed upon the nether side of its central enlargement. This valve is adapted to close upon the seat 53a. l

It will be observed that the metering pins 5Ia and 5Ib are convexly tapered in opposite directions. In this manner, the pin 5Ia will allow increasing passage of pressure uid; while the other pin 5I b will throttle the flow thereof as the valve 5Ic approaches its seat 53a.

During the flowing operation, the pressure fluid enters the device through the openings 33h and thence passes into the tubing I via the baille chamber 33e, the chamber 52h, the opening 53h,

the chamber 31a, and the opening 3| b;

The chamber 62a may be lled with a lubricant. The ring valve 4| is engaged with the enlargement 54a and with a seat surrounding the opening 3 la. This valve has large clearance with the shell 52 in order that part of the lubricant within the shell 82 can pass around the member 4| when the valve 5|c travels toward its seat 53a.

The ball floor member 55, having the tubular extens'ion 55a formed at its upper end into the ball oor 55h, has threaded engagement within the shell 52. 'I'he latch may be adjusted by screwing the member 55 upwardly or downwardly. any position thereof being securable by the lock ring 58. The latch balls 45 are engaged by the confronting sloping surfaces of the ball roof 43 and the ball oor 5517. These inclined surfaces and the force of the spring 42 urge the latch balls inwardly so that they will engage within the latching recess 36e when the valve 5|c engages upon its seat 53a.

n the downward stroke of the rod 54, the lubricant within the chamber 55d will be forced out through the openings 55e thereby expanding the slight annular leaf spring check valve 51 far enough to permit such escape of the lubricant. The lower end of the rod 54 has slight clearance within the chamber 55d in order that it will exert an alternate piston driving and suction force upon the lubricant under it. The pins 55, secured within the tubular extension 55a, prevent the leaf spring 51 from becoming vertically displaced. This spring has slight clearance between the threaded base of the member 55 and the pins 56. The lubricant may circulate freely through the latch because of the ample clearance between the ball iioor 55b and the shell 52, the considerable space between the balls 45 and the large clearance between the ball roof 43 and the rod 35.

Itis apparent that duringk the downward movement of the valve 5|c the rod 54 will move freely, because the thin leaf spring 51 will yield easily to the lubricant escaping through the openings 55c, but after the valve 5|c seats, its opening will be resisted by the force of the engaged latch. After the latch releases, the upward movement of this valve will be retarded by the suction of the rod 54 within the closely conforming chamber 55d. The rod 54 then tends to pull a vacuum within the chamber 55d, because the leaf spring 51 closes the openings 55e on the upstroke of the plunger 5|.

It will be observed that the pressure fluid entering the device through the openings 33h is prevented by the baille 34a from abrading the rod 50 and the metering pin 5|a.

If it be desired to cause the valve 5|c to close suddenly, the latch balls may be engaged normally upon another latching surface similar to the recess 36e, as appears in Fig. 11.

If it is not desired to meter the pressure fluid,

' it is apparent that the metering sleeve 1 may be omitted in Figs. 1 and 3. For the same purpose, the piston 28 in Fig. 9 may be of reduced outside diameter. Likewise, metering may be avoided in Fig. by expanding the chambers 34h and 35h to the diameter of the straight portion 34d. The same result may be obtained in Fig. 11 by reduc'- ing the diameters of the metering pins 5|a and 5| b.

Either ofthe iiow devices herewith shown may beinstalledin awell, as appears in Fig. 18, where- 11. Increasing differential will quickly close the' in the well casing 53 has the tubing 58 centrally 75 from the intake nipple 12 to the bottom of the well 15. l Production from the formation 18 enters the casing through the gun perforations 59 and rises to the normal level 13.

Now. to ilow the Well, pressure fluid will be turned into the annular space 11 via the pipe line 51. The upper end of the tubing 55 beingy open, there will be no resistance in the tubing. Pressure will rise rapidly in the annular space diiferential valves in the ow devices 55A. 'I'he normal liquid level 13 will change to the depressed liquid level 14 in the annular space 11 and to the upstanding liquid level 15 in the tubing. 'I'he i'low devices 55A proxlmately above the depressed liquid level 14 will be open and intaking pressure iluid, each device being uncovered in the open position as the depressed liquid level 14 is lowered by owing, while, at the same time, the device next above the open one will be closing or closed according to the differential obtaining there.

In Fig. 16, I show a surface intermitter adapted to be employed in conjunction with flow devices and which can be adjusted to open the tubing valve 18 at any desired pressure within the annular space 11 and to close the tubing Valve at any appreciably lesser pressure. 'I'he valve 18, threadedly joined into the tubing 55 proxlmately above the casing head 54, has a depending arm 18a adapted to be rotated for the purpose of opening and closing the valve. This arm has a straight pin 19 secured transversely through it and slidable within the spiral slots a of the shell 80, there being two of these slots receiving opposite ends of the pin 19; the cap 8 I, threadedly engaged over the shell 80, being 'employed to house the ends of the pin and the slots 80a.

The tubular bracket 90 supports the lubricator shell 9|, having within it the lubricator cup 92 containing the lubricant 93. The cylinder 91 is threadedly joined into an internal boss 9|b and made leakproof in its connection therewith by the stuffing box |00.

The latch 95 normally engages the groove 94a by force of the coiled spring 99 housed within the cylinder 91 closed by the cap 98. The latch shaft |05 has threaded connection with the piston 94 and is adapted to have its groove |05a engaged by the latch |03, housed Within the cylinder |08, this latch being operated by the coiled spring |04.

The bracket 81 positioned upon the tubing 65 by the U bolts 85 and the bracket 89 positioned upon the tubing by the U bolts 88 secure the intermitter assembly upon and in alignment with the tubing. The nut 95 secures the cylinder 91 within thebracket 89. The cap |01 secures the lower end of the cylinderv|08 within the bracket 81 and the cap |09 closes the upper end. I

The spiral shell carrier 82 has the shell 80 secured between its forked end by the nut 84. The sleeve |02, slidably engaged about the shaft |08, has the opposite slots |02a which slidably engage the arms 82a and 82h of the member 82.

When a predetermined pressure fluid force builds up within the annular space 11, this force will communicate through the tubular bracket 90 to the lower end of the` piston 94 via the openings 92a, 82h, and 81a, and spring the latch 95; whereupon the shell carrier 82 will be forced upward, causing the pin 19 to rotate the valve arm 18a by means of the spiral slots 80a. This movement compresses the spring IM and causes the'latch |03 to engage the groove |06a. In this operation, the lubricant 93 follows the piston and lubricates the cylinder 91 and the cups 94b secured upon the lower end of the piston 94.

The dashpot cushions the upstroke of the piston 94 so as to preventl a hammering action upon the valve.

When, in the process of flowing the well, the pressure iluid force within the annular space 11 decreases to a predetermined value, the expansive iforce of the compressed spring |01 will spring the latch |03 and return all parts to the position shown in Fig. 16.

'I'he ilnger 83, secured between the shell carrier 82 and the nut 84, is adapted to operate a mechanical counter 85 each time the valve 18 is opened.

Preferably the device in each of its embodiments should be installed as shown on the drawings with respect to the up and down position thereof. Accordingly upward and downward directions \will be understood as corresponding to those shown in the drawings.

It is apparent that many minor mechanical changes and substitution of other parts for those shown can be made within the scope of the stated objects and appended claims.

What is claimed is:

l. A well flowing device comprising a tubular body having a passageway in the wall thereof with an inlet and an outlet, a valve assembly movable in and adjacent said passageway and including a valve rod extending longitudinally of the passageway, a valve on said rod, a valve seat in the passageway adapted to be engaged by the valve, means normally urging the assembly axially of the passageway to maintain the valve and valve seat in spaced relation, a piston on said rod subjected to pressure fluid'about the body and tending to move the valve to closed position,

a second piston on the rod, and a pressure passage to said second piston from areduced pressure chamber between the inlet and the valve seat.

2. A well flowing device comprising a tubular body having a chamber in the wall thereof with an inlet and an outlet providing a passage through the chamber from the exterior to the interior of the body, a valve assembly in said chamber, said assembly including a rod having a valve thereon, a valve seat in said passage adapted to be engaged by said valve, spaced pistons onsaid rod, a metering sleeve attached to one of said pistons, said sleeve Vbeing slidable within said chamber and having a metering recess with lateral openings to meter pressure fluid from the inlet to the interior of the chamber, and spring means normally urging the valve assembly axially of the chamber to move the valve away from said seat.

3. A well Qflowing device comprising a tubular body having a chamber with an inlet and an outlet providing a passage through the chamber from the exterior to the interior of the body, a valve assembly in said chamber including a rod having a pressure fluid control valve thereon, a valve seat in said passage adapted to be engaged by said valve, spaced pistons on said rod subjected respectively to the pressure interiorly and exteriorly of the body, a support nipple in said chamber intermediate said pistons, a leaky check valve in said nipple, a body of lubricant in the chamber between said pistons, said check valve being adapted to delay the opening of the pressure iiuid control valve, and a spring in said chamber urging the pressure fluid control valve toward its seat.

4. A nipple adapted to be connected into the tubing of a well, a shell attached to said nipple,

'said shell having a chamber with an inlet and an outlet providing a passage through said chamber from the exterior of said shell to the interior of said nipple, a piston assembly in said shell, said assembly including spaced pistons, subjected respectively to pressure interiorly and exteriorly of said shell, a lubricant in the shell between said pistons, a rod connecting said pistons and extending from one of said pistons and having its end formed into a valve, a metering sleeve attached to one of said pistons, said sleeve being slidable within said shell and having a metering recess with lateral openings therethrough adapted to admit pressure fluid from the inlet openings in said shell, a seat in said chamber from which said valve normally is spaced and adapted to be engaged'thereby, a support nipple secured in said shell between the pistons, a check valve in said nipple, said valve being spaced slightly from its seat, a spring urging said valve toward said seat, a one-way passage for said lubricant through said nipple, said passage being controlled by said check valve which thus is adapted to delay the opening of said pressure fluid control valve, and openings communicating between the pistons most remote from said valve and the exterior of said shell. 5. In a well flowing device the combination of body having a chamber therein, a passage from said chamber to the interior of the body, a valve assembly in said chamber, said assembly including piston means subjected to the pressure interiorly and exteriorly of the body, an inlet to said chamber from the exterior of the body so that pressure fluid exerting a pressure upon the piston means may be admitted through said chamber and passage to the interior of the body, a metering sleeve attached to said piston means and slidable therewith proximate said inlet, said metering sleeve being adapted to supply pressure from the interior of the body to one side of the piston means, and having a metering recess adapted to move into mating relation with said inlet, and means for controlling the position of the valve assembly in accordance with the differential pressure between the exterior and interior.

ALEXANDER BOYNTON. 

